CN103835940A - Variable displacement oil pump - Google Patents

Abstract

A variable displacement oil pump can restrain the excessive rise of discharge pressure even the revolving speed of a pump increases in the presence of the requirement for maintenance of desired discharge pressure. The variable displacement oil pump includes: an electromagnetic switching valve (40) arranged to switch a state in which the hydraulic fluid is introduced to a second control hydraulic chamber (32) through an intermediate passage (60) from branch passages (3, 4), and a state in which the hydraulic fluid is discharged from the second control hydraulic chamber through the intermediate passage; and a pilot valve (50) which supplies or cuts off discharge pressure for a first control hydraulic chamber (31) according to the discharge pressure and supplies or cuts off discharge pressure for the second control hydraulic chamber (32) through the electromagnetic switching valve and the intermediate passage. When the discharge pressure of a discharge channel is higher than the required discharge pressure, the pilot valve supplies the discharge pressure for the first control hydraulic chamber and then discharges working oil in the second control hydraulic chamber.

Description

Variable capacity type oil pump

Technical field

The present invention relates to the variable capacity type oil pump of for example automobile engine.

Background technique

In recent years, for the oil of discharging from oil pump is required to discharge for the variable valve gear of the acting characteristic of each slide part of such as internal-combustion engine, controlling combustion engine valve etc. the different equipment of pressing, require the low pressure property of the first speed range and two stage characteristics of the high pressure characteristics of the second speed range.

In order to meet this requirement, the variable displacement pump that for example patent documentation 1 is below recorded has been considered following technology: by overcome spring members spring energized move to change with respect to the outer circumferential face side of the cam ring of the offset of rotor be provided with two opposed compression chambers, make pump discharge to be pressed with and selectively act on these compression chambers, make thus described cam ring work with two stages.

Patent documentation 1:(Japan) special table 2008-524500 communique

But, the variable displacement pump of described patent documentation 1 need to utilize described spring members that spring constant is larger to the described cam ring application of force, therefore, with respect to discharging the rising of pressing, cam ring reduces to the mobility of the little direction of offset, want to maintain the first discharge pressure or second and discharge pressure, along with revolution speed rises, discharge pressure and will significantly rise.Consequently, produce technical problems such as departing from requirement discharge pressure characteristic.

Summary of the invention

The present invention, in view of the technical problem of above-mentioned existing variable capacity type oil pump proposes, when its object is that the discharge that provides a kind of requirement to maintain hope is pressed, also can suppress to discharge the variable capacity type oil pump of the excessive rising of pressing even if revolution speed rises.

In order to achieve the above object, first aspect present invention provides a kind of variable capacity type oil pump, it is characterized in that possessing:

The rotor being driven in rotation;

Multiple blades, it is come in and gone out and is located at freely the periphery of this rotor;

Cam ring, it holds described rotor and blade and forms multiple pump chambers in inner circumferential side, and, change the center of inner peripheral surface with respect to the offset of the rotating center of described rotor by mobile;

Sucting, the described pump chamber opening that when it carries out eccentric move with respect to the rotating center of described rotor to a direction to described cam ring, volume increases;

Discharge portion, the described pump chamber opening of volume reducing it carries out eccentric movement during to described cam ring to other direction;

Force application part, its to described cam ring with respect to the large direction of the eccentric quantitative change of the rotating center of described rotor to the described cam ring application of force;

First controls grease chamber, and it is given described cam ring and make the other direction that described cam ring diminishes to offset carry out eccentric mobile power by importing via importing path the application of force that discharge pressure is resisted described force application part from described discharge portion;

Second controls grease chamber, and it cooperates with the application of force of described force application part by being imported into working oil, gives the power that described cam ring is moved to a direction;

Switching mechanism, it switches to via the access that is communicated with described discharge portion and the second control grease chamber and controls to described second the state that grease chamber imports the state of working oil and discharges working oil via described access from the second control grease chamber;

Become the work of minimum advancement row at the offset of described cam ring, along with described discharge presses change large, the opening area of described access changes, and discharges the described second opening area of controlling the drain passageway of the working oil in grease chamber and is changed to contrary with the opening area of described importing path.

On the basis of first aspect, the variable capacity type oil pump of second aspect is characterised in that,

Described switching mechanism is by the solenoid electric valve of electric switching controls.

A kind of variable capacity type oil pump of third aspect present invention, is characterized in that possessing:

The rotor being driven in rotation;

Multiple blades, it is come in and gone out and is located at freely the periphery of this rotor;

Cam ring, it holds described rotor and blade and forms multiple pump chambers in inner circumferential side, and, by moving the center that changes inner peripheral surface with respect to the offset in the rotation of described rotor;

Sucting, the described pump chamber opening that when it carries out eccentric move with respect to the rotating center of described rotor to a direction to described cam ring, volume increases;

Discharge portion, the described pump chamber opening of volume reducing it carries out eccentric movement during to described cam ring to other direction;

Force application part, its to described cam ring with respect to the large direction of the eccentric quantitative change of the rotating center of described rotor to the described cam ring application of force;

First controls grease chamber, and it presses the application of force of resisting described force application part by being imported into from described discharge portion to discharge, and gives described cam ring and makes the other direction that described cam ring diminishes to offset carry out eccentric mobile power;

Second controls grease chamber, and it cooperates with the application of force of described force application part by being imported into working oil, gives the power that described cam ring is moved to a direction;

Switching mechanism, it switches to via the access that is communicated with described discharge portion and the second control grease chamber and controls to described second the state that grease chamber imports the state of working oil and discharges working oil via described access from the second control grease chamber;

Control mechanism, comprise: valve body, it is formed with respectively the introducing port that imports described discharge and press, control with described first that grease chamber is communicated with first control mouthful, the second control mouth being communicated with via described access and described the second control grease chamber side, the connecting port being communicated with the described switching mechanism side of described access, the drain tap that can be communicated with the second control mouth; Guiding valve, it is located in this valve body sliding freely, controls the connected state of each mouthful; Control spring, its with than the little application of force of the application of force of described force application part to a direction to this guiding valve application of force;

At described guiding valve by the described control spring application of force and to a direction the largest mobile initial position, become described introducing port by this jammed spool valve, and described first controls mouth and drain tap connection, described second controls the first state of mouth and connecting port connection, discharge to press and increase and oil pressure in described introducing port uprises, when the application of force that described guiding valve is resisted described control spring thus moves to other direction, become described introducing port and the first control mouthful connection, and the second state of described the second control mouth and drain tap connection;

When the spring force of resisting described control spring when described guiding valve moves to other direction, be changed to the opening area of controlling mouthful with described first to contrary size from the described second opening area of controlling mouthful circulation flow path to drain tap.

On the basis of the third aspect, the variable capacity type oil pump of fourth aspect is characterised in that,

Under described the second state, when the spring force of resisting described control spring when described guiding valve moves to other direction, the described first opening area of controlling mouthful changes in the mode diminishing, and becomes large from the described second opening area of controlling mouthful circulation flow path to drain tap.

On the basis of fourth aspect, the variable capacity type oil pump of the 5th aspect is characterised in that,

Under described the second state, when the spring force of resisting described control spring when described guiding valve moves to other direction, the described first opening area of controlling mouthful changes in the mode diminishing, and is controlling mouthful to the circulation flow path opening of drain tap from described second, and it is large that this opening area becomes.

On the basis aspect the 5th, the variable capacity type oil pump of the 6th aspect is characterised in that,

Under described the second state, resist the spring force of described control spring and other direction while moving when guiding valve, the described first opening area of supplying with exhaust port diminishes and closes, afterwards, from described the second control mouthful circulation flow path opening to drain tap, and its opening area changes to become large mode.

On the basis aspect the 6th, the variable capacity type oil pump of the 7th aspect is characterised in that,

The oil of discharging from described discharge portion is the lubrication oil of internal-combustion engine.

On the basis aspect the 7th, the variable capacity type oil pump of eight aspect is characterised in that,

The oil of discharging from described discharge portion be internal-combustion engine variable valve gear valve driving oil and sprayed and for the cooling oil of piston by oil nozzle.

On the basis of the third aspect, the variable capacity type oil pump of the 9th aspect is characterised in that,

Described guiding valve is formed with the via hole of the hollow shape of an axial distolateral opening, this via hole open one distolaterally dispose described control spring, and, be communicated with described via hole from being radially formed through in another distolateral through hole, form from described second and control mouth to the circulation flow path drain tap by this through hole and via hole.

A kind of variable capacity type oil pump of tenth aspect present invention, is characterized in that possessing:

Pump structure body, it discharges by being driven in rotation the volume-variation that makes multiple work grease chamber the oil being imported into from sucting from discharge portion;

Changeable mechanism, it moves by movable member, changes to the volume-variation amount of the described work grease chamber of described discharge portion opening;

Force application part, its under the state of giving described movable member load on spring to the large direction application of force of volume-variation quantitative change of the described work grease chamber at described discharge portion opening;

First controls grease chamber, and it is pressed by being imported into from the discharge of described discharge portion, makes the masterpiece of direction of the application of force of resisting described force application part for described changeable mechanism;

Second controls grease chamber, and it makes with the equidirectional masterpiece of the application of force of described force application part for described changeable mechanism by being imported into working oil;

Switching mechanism, it switches to and imports the state of controlling the working oil in grease chamber than the state of the working oil of described discharge pressure decompression and discharge described second from described discharge portion to the second control grease chamber;

Control mechanism, has: first throttle portion and the second restriction, and described first throttle portion utilizes described changeable mechanism to become the work of minimum advancement row in the volume-variation amount of described work grease chamber, becomes large along with discharging to press, and orifice size is increased; Described the second restriction reduces orifice size;

Utilize the side in described first throttle portion and described the second restriction, carry out throttling to controlling to described second the working oil of supplying with grease chamber from described switching mechanism, utilize the opposing party to carry out throttling to controlling the working oil of discharging to low voltage section grease chamber from described second.

The present invention the tenth a kind of variable capacity type oil pump on the one hand, is characterized in that possessing:

The rotor being driven in rotation;

Multiple blades, it is come in and gone out and is located at freely the periphery of this rotor;

Cam ring, it holds described rotor and blade and forms multiple pump chambers in inner circumferential side, and by moving the center that changes inner peripheral surface with respect to the offset in the rotation of described rotor;

Sucting, the described pump chamber opening that when it carries out eccentric move with respect to the rotating center of described rotor to a direction to described cam ring, volume increases;

Discharge portion, the described pump chamber opening of volume reducing it carries out eccentric movement during to described cam ring to other direction;

Force application part, its to described cam ring with respect to the large direction of the eccentric quantitative change of the rotating center of described rotor to the described cam ring application of force;

First controls grease chamber, and it is given described cam ring and make the other direction that described cam ring diminishes to offset carry out eccentric mobile power by importing via importing path the application of force that discharge pressure is resisted described force application part from described discharge portion;

Second controls grease chamber, and it cooperates with the application of force of described force application part by being imported into working oil, gives the power that described cam ring is moved to a direction;

Switching mechanism, it switches to via the access that is communicated with described discharge portion and the second control grease chamber and controls to described second the state that grease chamber imports the state of working oil and discharges working oil via described access from the second control grease chamber;

Control mechanism, its discharge according to described discharge portion presses to the first control grease chamber and supplies with discharge pressure or sever supply, and controls grease chamber via described access to described second and supply with or discharge oil pressure;

Described control mechanism is configured to, in the case of the discharge pressure ratio of described discharge portion require to discharge press high, supply with to discharge to the first control grease chamber and press, and, the working oil in the second control grease chamber is discharged.

According to the present invention, exist maintain hope discharge press require time, even revolution speed rise, also can suppress discharge press excessive rising.

Accompanying drawing explanation

Fig. 1 is the schematic diagram that has represented to use the oil hydraulic circuit of the oily supply system of the variable capacity type oil pump of embodiment of the present invention;

Fig. 2 is the overall schematic of the variable capacity type oil pump of described mode of execution, is the figure that represents the state of the offset maximum of the cam ring of oil pump;

Fig. 3 is the sectional arrangement drawing of the oil pump that provides of present embodiment;

Fig. 4 is the plan view of the pump housing that represents that present embodiment provides;

Fig. 5 is the sectional drawing that represents the installment state of electromagnetic switching valve that present embodiment provides and the second oil purifier;

Fig. 6 represents the internal-combustion engine rotational speed of the existing variable capacity type oil pump without pilot valve and the plotted curve of the relation that pump discharge is pressed;

Fig. 7 is the job description figure of the variable capacity type oil pump of present embodiment;

Fig. 8 is the job description figure of described variable capacity type oil pump;

Fig. 9 is the job description figure of described variable capacity type oil pump;

Figure 10 is the internal-combustion engine rotational speed of variable displacement pump and the plotted curve of the relation that pump discharge is pressed that represents described mode of execution;

Figure 11 (A), (B), (C) represent to change present embodiment provides the first major component amplification profile while supplying with the relative size of the opening area of exhaust port and the first shoulder face width degree of guiding valve;

Figure 12 (A), (B), (C) represent to change the first circular bead surface shape of the guiding valve that present embodiment provides and the width and first that the changes central position major component amplification profile while supplying with the relative size of opening area of exhaust port.

Symbol description

04: drain passageway

05: main oil gallery

1: the first oil purifier

2: the second oil purifiers

3: the first tributary circuits

4: the second tributary circuits

5: draining path

6: supply with drain passageway

10: oil pump

11: the pump housing (shell)

12: cap assembly (shell)

13: pump accommodating part

14: live axle

15: rotor

16: blade

17: cam ring

18: spring (force application mechanism)

20: pump chamber (work grease chamber)

21: suction port (sucting)

22: exhaust port (discharge portion)

25a: the first intercommunicating pore

25b: the second intercommunicating pore

Control grease chamber at 31: the first

Control grease chamber at 32: the second

33: the first compression faces

34: the second compression faces

40: electromagnetic switching valve (switching mechanism)

50: pilot valve (control mechanism)

51: valve body

52: slide and use hole

53: guiding valve

53a: the first circular bead surface

53b: the first path axial region

53c: the second circular bead surface

53e: the second path axial region

53f: the 3rd circular bead surface

53g: the first annular slot

53h: the second annular slot

53j: through hole

55: first pilot introducing port

56: connection mouth

57a: first supplies with exhaust port (first controls mouth)

57b: second supplies with exhaust port (second controls mouth)

58: drain tap

60: via intermedia

Embodiment

Below, based on accompanying drawing, the mode of execution of variable displacement pump of the present invention is described in detail.It should be noted that, present embodiment represents to be applicable to the situation of variable capacity type oil pump, this variable capacity type oil pump can be used as the operation source of the variable valve actuator for air of the air valve correct-timing variable of the engine valve that makes automobile engine, and utilize oil nozzle to the slide part of internal-combustion engine, particularly to the slide part supplying lubricating oil in piston and cylinder hole, and to the bearing supplying lubricating oil of bent axle.

Fig. 1 has represented to use the oil hydraulic circuit of the variable capacity type oil pump of present embodiment, variable capacity type oil pump 10 utilizes the rotary driving force being passed from the bent axle of internal-combustion engine to be rotated, be stored in the oil of food tray 01 via filter screen 02 from sucking path 03 suction, then be that drain passageway 04 is discharged to the main oil gallery 05 of internal-combustion engine from discharge portion.

In the overflow passage 06 of described drain passageway 04 branch, be provided with pump and discharge while pressing excessively rising, make oil return to the spherical non-return relief valve 07 in food tray 01.

Described main oil gallery 05 is to the oil nozzle and the Ventilsteuerzeitsteuervorrichtung that for example piston of the slide part of described internal-combustion engine are sprayed to cold oil, the bearing of bent axle is for oil supply, and the first oil purifier 1 of the foreign matter in the upstream side of drain passageway 04 side is provided with the oil that traps circulation, also be provided with in addition the shunt access 08 that described first oil purifier 1 of main oil gallery 05 is shunted, and in this shunt access 08, be provided with spherical non-return diverter valve 09, in the time that described the first oil purifier 1 occurs for example to stop up and is difficult to carry out oily circulation, this spherical non-return diverter valve 09 is opened, make oil flow into downstream side via shunt access 08.

In addition, than the first oil purifier 1 of described main oil gallery 05 more downstream branch have the first tributary circuit 3.The downstream side of this first tributary circuit 3 is pilot valve 50 via control mechanism and is communicated with the first control grease chamber 30 described later of described oil pump 10 for supplying with drain passageway 6a via first, and there is the second tributary circuit 4 in branch halfway.This second tributary circuit 4 is provided with switching mechanism in downstream side be electromagnetic switching valve 40.This this electromagnetic switching valve 40 is connected with described pilot valve 50 via via intermedia 60, and described in this, pilot valve 50 is communicated with the second control grease chamber 31 described later of described oil pump 10 via the second supply drain passageway 6b.

Described electromagnetic switching valve 40 by not shown controller unit connect (energising) ?cut off (non-energising) and control, make described the second tributary circuit 4 and supply with drain passageway 60 to be communicated with, or this supply drain passageway 60 and draining path 5 are communicated with.Concrete structure etc. will be narrated in the back.

In addition, near described the first tributary circuit 3 and branching portion main oil gallery 05 branch, be provided with the second oil purifier 2.As shown in Figure 5, this second oil purifier 2 is made up of roughly main body 2a cylindraceous, the metal that the has round-ended cylinder shape wet end 2b processed that is combined in an end of this main body 2a of the branch part that is pressed into the first tributary circuit 3 that is fixed on main oil gallery 05 and large footpath, and the pollutant that particularly prevents from sneaking in oil flows into described electromagnetic switching valve 40.

These first, second oil purifiers 1,2 use respectively for example filter paper or metal wet end, in the situation that filter paper or wet end have occurred to stop up etc., can change cartridge type wet end or filter paper.In addition, the mesh of the wet end 2b of described the second oil purifier 2 is larger than the bore of the mesh of the wet end of the first oil purifier 1.

Described oil pump 10 is located at the front end of the cylinder block 35 of internal-combustion engine etc., as shown in Figure 2 to 4, possess: shell, it is by forming in the mode of one end side opening and the pump housing 11 of the inner cross section コ shape with the pump accommodating chamber 13 being made up of columned space and the cap assembly 12 that seals an end opening of this pump housing 11 form; Live axle 14, it is rotatably freely supported on this shell, connects the approximate centre portion of pump accommodating chamber 13 and utilizes the bent axle of internal-combustion engine to be rotated driving; Pump structure body, it is contained in pump accommodating chamber 13 and the rotor 15 of central part and live axle 14 combinations and discrepancy is contained in multiple slit 15a of peripheral part that notch shape is radially formed in this rotor 15 freely respectively blade 16 form by rotating freely; Cam ring 17, its rotating center with respect to rotor 15 is disposed at the outer circumferential side of this pump structure body eccentricly, is pump chamber 20 with being divided into multiple work grease chamber together with the blade 16,16 of rotor 15 and adjacency; Force application part (control spring) is spring 18, and it is housed inside in the pump housing 11, and the direction always increasing with respect to the offset of the rotating center of rotor 15 to cam ring 17 is to these cam ring 17 application of forces; A pair of ring portion 19,19, its both sides and diameter of inner circumferential side that is disposed at sliding freely rotor 15 is less than the diameter of this rotor 15.

The described pump housing 11 is integrally formed by aluminum alloy material, also has diagram in Fig. 3 and Fig. 4, in the substantial middle position of the bottom surface of pump accommodating chamber 13 13a, is formed through and rotates the bearing hole 11a of an end of supporting driving shaft 14 freely.In addition, as shown in Figure 4, becoming the assigned position of inner circle wall of pump accommodating chamber 13 of inner side surface of the pump housing 11, otch is formed with the bearing hole 11b that inserts fixing swing and support freely the pivot pin 24 of cam ring 17.In addition, at the inner peripheral surface of described bearing hole 11a, be formed with the lubricated maintenance groove 11e that oil is kept and provided described live axle 14.

In addition, on the inner circle wall of pump accommodating chamber 13, the straight line that clips link bearing hole 11a center and bearing hole 11b center (is called " cam ring reference line " below.) both sides of M, be formed with first, second sealed sliding junction 11c, 11d that the sealed member 30,30 of the peripheral part that is disposed in cam ring 17 slips respectively.As shown in Figure 4, these each sealed sliding junction 11c, 11d are formed as from the center of bearing hole 11b planar by the radius R 1 stipulating, circular arc that R2 forms respectively, and be set as within the scope of the eccentric swing of cam ring 17 circumferential lengths that described each sealed member 30,30 always can slip.Thus, in the time that cam ring 17 carries out eccentric swing, by slide-and-guide, obtain the smooth work (eccentric swing) of this cam ring 17 along described each sealed sliding junction 11c, 11d.

In addition, on the 13a of the bottom surface of described pump accommodating chamber 13, as shown in Figures 2 and 4, in the outer regions of bearing hole 11a, with clamp respectively bearing hole 11a roughly opposed mode otch be formed with suction port 21 and exhaust port 22, described suction port 21 is to follow the pumping action of described pump structure body and the sucting of the roughly circular arc concavity that the mode of region (suction region) opening that increases to the internal capacity of pump chamber 20 forms, described exhaust port 22 is to follow the pumping action of described pump structure body and the discharge portion of the roughly circular arc concavity that the mode of region (discharging area) opening that reduces to the internal capacity of pump chamber 20 forms.

The diapire that described suction port 21 connects the pump housing 11 is formed with inlet hole 21a to outside opening, and described inlet hole 21a extends and arranges to spring accommodating chamber 28 sides described later from the substantial middle position of this suction port 21.Thus, be stored in the negative pressure that the lubricate oil base of the food tray 01 of internal-combustion engine produces in following the pumping action of described pump structure body, be inhaled into each pump chamber 20 in described suction region via inlet hole 21a and suction port 21.

In addition, described inlet hole 21a forms in the mode of the outer regions of the cam ring 17 towards pump suction side, sucks and presses to the outer regions guiding of the pump suction side of this cam ring 17.Thus, become to suck with the outer regions of the cam ring 17 of the pump suction side of each pump chamber 20 adjacency in described suction region and press or atmospheric low voltage section, thereby suppress lubricant oil from sucking each pump chamber 20 in region to the leakage of the outer regions of the cam ring 17 of pump suction side.

The upper position opening of described exhaust port 22 in Fig. 4 is formed with the tap hole 22a as one of discharge portion, and this tap hole 22a connects the diapire of the pump housing 11 and is communicated with described main oil gallery 05 via described drain passageway 04.

According to this structure, utilize the pumping action of described pump structure body and oil pressurized and that discharge from each pump chamber 20 of described discharging area, be supplied to main oil gallery 05 via exhaust port 22 and tap hole 22a, be re-supplied to each slide part and Ventilsteuerzeitsteuervorrichtung etc. in internal-combustion engine.

As shown in Figure 3, described cap assembly 12 is roughly tabular, the position corresponding with the bearing hole 11a of the pump housing 11 of lateral part is formed as cylindric, and on the inner peripheral surface of this cylindrical part, is formed through and rotates another distolateral bearing hole 12a of supporting driving shaft 14 freely.This cap assembly 12 utilizes multiple bolts 26 to be arranged on the open end of the pump housing 11.

In addition, the inner side surface of cap assembly 12 becomes general planar shape, but also the same with the bottom surface of the pump housing 11, can form suction, exhaust port 21,22.

Described live axle 14 is to utilize the rotating force being passed from bent axle that rotor 15 is formed to the right handed mode Fig. 2.

As shown in Figure 2, described rotor 15 otch are formed with described seven the slit 15a that form radially from inside center side direction radial outside, and, at the inner side of this each slit 15a base end part, be formed with respectively the back pressure chamber 15b of the cross section circular shape that imports the discharge oil that is discharged to described exhaust port 22.Thus, described each blade 16 utilizes the centrifugal force of ring portion 19,19 and the oil pressure of back pressure chamber 15b of the rotation of following rotor 15 to be pushed out to foreign side.

Each front-end face of described each blade 16 slips with the inner peripheral surface of cam ring 17 respectively, and the interior edge face of each base end part respectively with the outer circumferential face sliding contact of each ring portion 19,19.Thus, even at the oil pressure of lower, the described centrifugal force of internal-combustion engine rotational speed or back pressure chamber 15b hour, also can utilize each inner side surface, the inner peripheral surface of cam ring 17, the sidewall of the blade 16,16 of outer circumferential face, the adjacency of rotor 15 is the bottom surface 13a of pump accommodating chamber 13 and the inner side surface of cap assembly 12 of the pump housing 11, divides described each pump chamber 20 liquid-tightly.

It is circular that described cam ring 17 utilizes so-called sintering metal to be integrally formed as, at the assigned position of peripheral part, chimeric and form the hinge portion 17a of the roughly circular arc concavity of eccentric swing fulcrum along being axially equipped with described pivot pin 24, and, in the position across the opposition side at cam ring 17 center with respect to this hinge portion 17a, along being axially equipped with the arm 17b being connected with described spring 18.

At this, in the described pump housing 11, be provided with spring accommodating chamber 28 in the mode being communicated with pump accommodating chamber 13 via the interconnecting part 27 of position of opposition side that is formed at described bearing hole 11b, in this spring accommodating chamber 28, hold and state to some extent spring 18.

This spring 18 with the setting load W elasticity of regulation remain on by described interconnecting part 27 extend to below the front end of the described arm 17b in spring accommodating chamber 28 and the bottom surface of spring accommodating chamber 28 between.Below the front end of described arm 17b, be equipped with the roughly circular-arc support projection 17c that is formed as engaging with the inner circumferential side of spring 18, utilize one end of this support projection 17c support spring 18.

Therefore, described spring 18 utilizes the elastic force based on described load on spring W, via described arm 17b, and direction (clockwise direction in Fig. 2) application of force that cam ring 17 is always increased to its offset.Thus, under the off working state of the cam ring 17 shown in Fig. 2, this cam ring 17 is in the state that is pushed to above the stop surface 28a below the upper wall that is formed at spring accommodating chamber 28 of the effect lower arm part 17b of the spring force of described spring 18, and to be held in its offset with respect to the rotating center of rotor 15 be maximum position.

Like this, extend and arrange to the opposition side of hinge portion 17a by arm 17b, and utilize spring 18 to carry out the application of force to the front end of this arm 17b, can produce moment of torsion to greatest extent to cam ring 17, so realized the miniaturization of spring 18, consequently, contributed to the miniaturization of pump itself.

In addition, at the peripheral part of described cam ring 17, project respectively and have with described first, the second sealed sliding junction 11c, the opposed mode of 11d form first, a pair of first of the cross section general triangular shape of secondary sealing area, the second 17d of sealing configuration portion, 17e, and, at this each sealing configuration 17d of portion, on the sealing surface of 17e, be formed with first of cross section essentially rectangular shape along axial cut-outs, the second sealing keeps groove, in this each sealing keeps groove, hold respectively while maintaining at cam ring 17 eccentric swing and each sealed sliding junction 11c, the described a pair of sealed member 30 that 11d is slidably connected, 30.

At this, described first, second sealing surface respectively from the center of described hinge portion 17a by forming than forming described each sealed sliding junction 11c, the radius R 1 of 11d, the smaller predetermined radius of R2 of answering in contrast, between this each sealing surface and described each sealed sliding junction 11c, 11d, be formed with respectively small clearance C.

Described each sealed member 30,30 by the fluorine resin material with for example low frictional behavior along cam ring 17 be axially formed as elongated straight line shape, utilize to be disposed in described each sealing and to keep the elastic force of the elastic member of the rubber system of the bottom of groove to be pushed to each sealed sliding junction 11c, 11d.Thus, always guarantee the good liquid-tight property of each control described later grease chamber 31,32.

And, becoming described pump and discharging the outer regions of the cam ring 17 of the hinge portion 17a side of side, as shown in Figure 2, between the outer circumferential face of cam ring 17 and the inner side surface of the pump housing 11, by the outer circumferential face of cam ring 17 and the inner side surface of hinge portion 17a, described each sealed member 30,30 and the pump housing 11, divide respectively and be formed with the first control grease chamber 31 and the second control grease chamber 32 across the both sides of described hinge portion 17a.

Control in grease chamber 31 described first, suitably being supplied to via described pilot valve 50 and the first intercommunicating pore 25a of being formed at the pump housing 11 sidepieces the pump that is discharged to described exhaust port 22 from described main oil gallery 05 and the first tributary circuit 3 discharges and presses, by the first compression face 33 forming towards this first outer circumferential face of controlling the cam ring 17 of grease chamber 31, resist the elastic force of described spring 18 and bear the oil pressure from described main oil gallery 05, as shown in Fig. 7 and Fig. 9, give oscillatory forces (locomotivity) to the direction (counter clockwise direction in Fig. 2) that the offset of cam ring 17 is reduced.

; this the first control grease chamber 31 always approaches the direction concentric with the rotating center of rotor 15 to cam ring 17 center via described the first compression face 33 be that the direction that offset reduces is carried out the application of force to cam ring 17, and the amount of movement control of the concentric direction to this cam ring 17 contributes.

On the other hand, control in grease chamber 32 described second, similarly via described pilot valve 50 and by connection, the cut-out work of electromagnetic switching valve 40, suitably import via the discharge that is formed through abreast described the second tributary circuit 4 being connected in the second intercommunicating pore 25b of the sidepiece of the pump housing 11 with the first intercommunicating pore 25a and press.

In addition, on the outer circumferential face of the cam ring 17 towards this second control grease chamber 32, be formed with the second compression face 34, act on this second compression face 34 by making to discharge to press, formation is to the power of the directive effect of the elastic force of secondary spring 18, thus, the direction (clockwise direction in Fig. 2) that to it, offset is increased cam ring 17 is given oscillatory forces.

At this, as shown in Figure 2, the compression area of described the second compression face 34 is set as less than the compression area of described the first compression face 33, the application of force that the application of force of the eccentric direction of the cam ring 17 that the application of force of the interior pressure based on the second control grease chamber 32, the application of force of spring 18 produce and the first control grease chamber 31 produce forms balance with the power relation of regulation, as mentioned above, the application of force of the oil pressure secondary spring 18 in the second control grease chamber 32.That is, described second controls grease chamber 32 makes the discharge pressure being supplied to as required act on the second compression face 34 via described electromagnetic switching valve 40 and pilot valve 50, and suitably the application of force of secondary spring 18, controls the amount of movement of cam ring 17 to eccentric direction thus.

In addition, the exciting curent of the controller unit of described electromagnetic switching valve 40 based on from controlling combustion engine, move according to the operating condition of internal-combustion engine, via this electromagnetic switching valve 40, described the second tributary circuit 4 and the second intercommunicating pore 25b are suitably communicated with or are cut off and be communicated with.

As shown in Fig. 2 and Fig. 5, described electromagnetic switching valve 40 is three-way switch valve, mainly comprises: valve body 41, and it is pressed into the valve receiving bore 35a in the sidewall that is fixed on the cylinder block 35 that is formed at internal-combustion engine, along inner shaft to being formed with working hole 41a; Valve seat 42, it is pressed into the front end of described working hole 41a, and central authorities are formed with the solenoid open pore 42a being communicated with the downstream side of the second tributary circuit 4; Metal ball valve 43, it leaves, takes a seat and is located at freely the inner side of this valve seat 42, and described solenoid open pore 42a is carried out to switch; Solenoid unit 44, it is located at the distolateral of valve body 41.

Described valve body 41 is in the upper end portion of perisporium side, from being radially formed through the connecting port 45 being communicated with described the second tributary circuit 4 via solenoid open pore 42a, and, in the underpart of perisporium side, from being radially formed through the drain tap 46 being communicated with described working hole 41a.

Described solenoid unit 44 in the enclosure portion holds and disposes not shown electromagnetic coil, fixed iron core, movable core etc., be provided with push rod 47 at the front end of this movable core, this push rod 47 slides with specified gap in described working hole 41a, and front end pushes described ball valve 43 or removes pushing.

Between the outer circumferential face of described push rod 47 and the inner peripheral surface of described working hole 41a, be formed with the path 48 of the tubular of the described connecting port 45 of suitable connection and drain tap 46.

To described electromagnetic coil, connect-cut off from the controller unit of internal-combustion engine and switch on or block energising.

; when from controller unit to described electromagnetic coil outputting cutting break signal (non-energising); described movable core utilizes the spring force of not shown Returnning spring to retreat and moves and utilize push rod 47 to remove the pushing of ball valve 43, opening described solenoid open pore 42a.Thus, as shown in Figure 8, Figure 9, ball valve 43 utilizes to compress into go to retreat to move from the discharge of the second tributary circuit 4 and makes the second tributary circuit 4 and supply with drain passageway 6 to be communicated with, supply with oil pressure to the second control grease chamber 32, one end sealing of described tubular path 48 is cut off to the connection of this tubular path 48 and drain tap 46 simultaneously.

On the other hand, when from controller unit to described electromagnetic coil output connection signal (energising), movable core is resisted the spring force of Returnning spring and is passed in and out movement, utilizes described push rod 47 to push described ball valve 43.Thus, as shown in Fig. 2, Fig. 7, ball valve 43 stops up solenoid open pore 42a, and connecting port 45 and tubular path 48 are communicated with.Thus, the second oil pressure of controlling in grease chamber 32 is discharged to food tray 01 from pilot valve 50 and via intermedia 60 by described connecting port 45, tubular path 48 and drain tap 46.

Described controller unit detects current internal combustion engine operation state according to the oil temperature of internal-combustion engine and water temperature, internal-combustion engine rotational speed and load etc., particularly below internal-combustion engine rotational speed is regulation time, to the electromagnetic coil outputting cutting break signal (non-energising) of described electromagnetic switching valve 40, in the situation that internal-combustion engine rotational speed is higher than regulation, output connection signal (energising).

But, even if internal-combustion engine rotational speed is for below regulation, when the situation that is high-load region at internal-combustion engine etc., also to electromagnetic coil outputting cutting break signal, supply with oil pressure to the second control grease chamber 32.

Therefore, described oil pump 10 substantially utilizes from main oil gallery 05 and is supplied to the first control interior pressure of grease chamber 31 of oil pressure and the offset of the spring energized control cam ring 17 of spring 18, and the variable quantity of internal capacity of the described pump chamber 20 of control pump while driving, thus, the discharge that obtains low voltage control oil pump 10 is pressed the state of characteristic and is applied the interior pressure of the second control grease chamber 32 and controlled the offset of cam ring 17 by described electromagnetic switching valve 40, and the discharge of high voltage control oil pump 10 is pressed these two kinds of the states of characteristic to discharge and pressed characteristics.

In addition, by described pilot valve 50 is set, can realize the described low voltage control of described oil pump 10 and the stabilization of high voltage control.

; as shown in Figure 2; described pilot valve 50 is provided with guiding valve 53 in the slip of inside that is formed at valve body 51 cylindraceous in hole 52 sliding freely; and; this guiding valve 53 being given under the state of the load on spring of the valve spring 54 of the application of force above in figure, stopper 49 is by the lower open end sealing of valve body 51.

Described valve body 51 is being positioned at the upper end open above hole 52 for described slip, be formed with described in relative aperture and slide with the little first pilot introducing port 55 in hole 52, this elder generation's pilot introducing port 55 and slide and described guiding valve 53 is not done to the used time at the oil pressure from described first pilot introducing port 55 with the step conical surface 51a between hole 52, becomes that spring force that this guiding valve 53 utilizes described valve spring 54 is biased upward and the face of taking a seat of taking a seat.

Be communicated with the first pilot introduction hole 55 of described valve body 51 via the second oil purifier 2 from the first tributary circuit 3 of described main oil gallery 05 branch.

Described valve body 51 with described slip with hole 52 towards perisporium on, along being radially formed through: first supplies with exhaust port 57a, its be via described first supply with that drain passageway 6a and first controls that grease chamber 31 is communicated with first control mouth; Second supplies with exhaust port 57b, it is to supply with drain passageway 6b and second via described second to control the second control mouthful that grease chamber 32 is communicated with, and, in this second opposite location of supplying with the more downside of exhaust port 57b, along being radially formed through the connection mouth 56 being connected with one end of described via intermedia 60.In addition, at the downside of this connection mouth 56, along being radially formed through the drain tap 58 that doubles as back pressure exhaust port.

Described guiding valve 53 is formed as the roughly cylindric of upper end obstruction, be formed with the via hole 53i of a part of holding valve spring 54 in the inside of described the first tributary circuit 3, this guiding valve 53 has: first pilot introducing port 55 sides i.e. the first circular bead surface 53a of uppermost side in figure, be formed at the first path axial region 53b of the downside of this first circular bead surface 53a, be formed at the second circular bead surface 53c of the downside of this first path axial region 53b, be formed at the axial second long path axial region 53e of the downside of this second circular bead surface 53c, be formed at the 3rd circular bead surface 53f of the downside of this second path axial region 53e.

Described the first circular bead surface 53a, the second circular bead surface 53c and the 3rd circular bead surface 53f set same diameter for, and each outer circumferential face and described slip keep micro-gap and slide with the inner peripheral surface in hole 52.

Described the first circular bead surface 53a has been formed as cup shape, above import the compression face that the discharge of described first pilot introducing port 55 presses and form as bearing, and, follow moving up and down of guiding valve 53 and first supply with exhaust port 57a described in switch.

Described the second circular bead surface 53c follows moving up and down of guiding valve 53 and second supplies with exhaust port 57b described in switch.

In the periphery of described the first path axial region 53b, be formed with the first annular slot 53g that forms cone-shaped ring shape, and in the periphery of the second path axial region 53e, be formed with roughly the second annular slot 53h cylindraceous.

Described the first annular slot 53g via the through hole 53j connecting radially, is communicated to the first path axial region 53b to slide with hole 52 and described drain tap 58 from via hole 53i.On the other hand, described the second annular slot 53h is suitably communicated with described the second supply exhaust port 57b and connection mouth 56 according to the sliding position of guiding valve 53.

It should be noted that, described valve spring 54 is set for less than the spring force of the spring of described oil pump 10 18.

Described via intermedia 60 connects the described connecting port 45 of electromagnetic switching valve 40 and the described connection mouth 56 of pilot valve 50.

Described first supplies with drain passageway 6a connects the first supply exhaust port 57a of pilot valve 50 and the first intercommunicating pore 25a of oil pump 10.Second supplies with drain passageway 6b connects the second supply exhaust port 57b of pilot valve 50 and the second intercommunicating pore 25b of oil pump 10.

It should be noted that, supply with drain passageway 6a by described the first tributary circuit 3 and described first pilot introducing port 55, the first supply exhaust port 57a and first and form importing path.

In addition, form access by described via intermedia 60 and connection mouth 56, the second supply drain passageway 6b and the second supply exhaust port 57b etc.

(effect of present embodiment)

The effect of described electromagnetic switching valve 40 and the pilot valve 50 of present embodiment is together described with the oil pressure characteristic of Figure 10 below.

Fig. 2 is the state in the region of the internal-combustion engine shown in Figure 10 from starting to low speed rotation a.Under this state, electromagnetic switching valve 40 is output from the connection signal of controller unit and becomes "on" position, and therefore, connecting port 45 and drain tap 46 are communicated with.

Described pilot valve 50 is owing to being low oil pressure under the internal-combustion engine slow-speed of revolution, the state of the face 51a that takes a seat described in the first circular bead surface 53a that therefore becomes guiding valve 53 is seated at.Now, the first control grease chamber 31 is communicated with drain tap 58 by the first supply drain passageway 6a, the first supply exhaust port 57a, the first annular slot 53g, through hole 53j and via hole 53i.On the other hand, the second control grease chamber 32 is communicated with the connecting port 45 of connection mouth 56 and electromagnetic switching valve 40, then is communicated with draining path 5 via drain tap 46 by the second supply drain passageway 6b, the second supply exhaust port 57b, the second annular slot 53h.

Therefore, the first control grease chamber 31 and second controls grease chamber 32 and is all communicated with drain tap 58,46, therefore can not be imported into oil pressure, cam ring 17 utilizes the spring force of spring 18 to maintain counter clockwise direction in figure, it is the maximum eccentricity amount of arm 17b and stop surface 28a butt, in the time that revolution speed rises, oil pressure is roughly proportional rising also.

Afterwards, in the time that the discharge pressure of main oil gallery 05 utilizes oil pump 10 to reach the P1 shown in Figure 10, oil pressure is above the first pilot introducing port 55 of pilot valve 50 acts on the first circular bead surface 53a of guiding valve 53, and the spring force that this guiding valve 53 is resisted valve spring 54 then moves back and moves to the position shown in Fig. 7.

Like this, when described guiding valve 53 declines when mobile, first pilot introducing port 55 and first is supplied with exhaust port 57a and is communicated with under by the state of throttling at opening area each other, and this first connection of supplying with exhaust port 57a and drain tap 58 is cut off, and imports first and controls grease chamber 31 thereby discharge to press.Therefore, the spring force of cam ring 17 antagonistic springs 18, starts as shown in the figure to counterclockwise in rotary moving and become the state of the low voltage control shown in the internal-combustion engine rotational speed b of Figure 10.

In not having as the existing variable capacity type oil pump of the pilot valve 50 of present embodiment, even under the state of described low voltage control, oil pressure characteristic is also as shown in the solid line of Fig. 6, in the time of oil pressure control, pump is discharged to press and is risen along with the rising of internal-combustion engine rotational speed, particularly further takes on and rises to the right from the state of the substantially vertical rising shown in c.In addition, in Fig. 6, low speed rotation region when a represents from engine starting, b represents low, middle rotary area, c represents High Rotation Speed region, and, VTC represents the Ventilsteuerzeitsteuervorrichtung of intake valve and exhaust valve, OJ represents to spray to piston the oil nozzle of cold oil, and CM represents the bearing of bent axle, clearly represents these requirement discharge pressure characteristics corresponding with internal-combustion engine rotational speed.

In contrast, as in the embodiment described in, be provided with in the situation of pilot valve 50, by utilizing this pilot valve 50 to control the oil pressure of the first control grease chamber 31, can suppress oil pressure and excessively rise.

In described pilot valve 50, decline if discharge to press too, guiding valve 53 utilizes the spring force of valve spring 54 to move to the direction of taking a seat, the same with afore-mentioned, utilize the first circular bead surface 53a to cut off first pilot introducing port 55 and first and supply with exhaust port 57a, and first supplies with exhaust port 57a is communicated with drain tap 58, reduced pressure in the first control grease chamber 31 and the offset that increases cam ring 17 makes oil pressure rising.

Under this state, rise if discharge to press too, described guiding valve 53 is resisted the spring force of valve spring 54 and is declined mobile to stopper 49 directions, making first pilot introducing port 55 and first supply with exhaust port 57a is communicated with, supply with oil pressure to the first control grease chamber 31 and reduce the offset of described cam ring 17, making to discharge drops.

These controls just can be carried out by the small movement of described guiding valve 53, so the impact of the spring constant of valve spring 54 is less, can will discharge pressure-controlled at P1 roughly.

Particularly described first pilot introducing port 55 and first is supplied with exhaust port 57a and is communicated with under the less state of opening area each other, and controlled by the state of the upper ora terminalis throttling of the first circular bead surface 53a of described guiding valve 53, therefore, can make described discharge press and stably remain on roughly P1.

Next, if internal-combustion engine rotational speed further rises, be cut off to the energising of described electromagnetic switching valve 40, as shown in Figure 8, in these electromagnetic switching valve 40 sides, described solenoid open pore 42a and connecting port 45 are communicated with, in pilot valve 50 sides, it is constant that described guiding valve 53 keeps that first pilot introducing port 55 and first is supplied with to the state that exhaust port 57a is communicated with a little, the spring force of opposing valve spring 54 declines mobile (throttle) on the other hand, maintains the connection of connection mouth 56 and the second supply exhaust port 57b via described the second annular slot 53e.

Therefore, control in grease chamber 32 in the first control grease chamber 31 and second, the discharge that all imports main oil gallery 05 from the first tributary circuit 3 and the second tributary circuit 4 is pressed, it is that the direction that eccentric quantitative change is large moves to clockwise direction that described cam ring 17 utilizes the spring force of spring 18 and the second oil pressure of controlling grease chamber 32 of auxiliary this spring force, thereby converts the state of the high voltage control shown in Figure 10 c to.Under the internal-combustion engine rotational speed shown in this Figure 10 c, even if switch to high voltage control, discharge pressure and also can not reach P2, therefore the offset of cam ring 17 becomes maximum again, discharges to press also and roughly rises pro rata with the rising of internal-combustion engine rotational speed.

Then,, in the time that discharge pressure reaches P2 because of the rising of internal-combustion engine rotational speed, as shown in Figure 9, the guiding valve 53 of described pilot valve 50 utilizes the spring force of the oil pressure opposing valve spring 54 that acts on first pilot introducing port 55 further to decline mobile.Therefore, connection mouth 56 and the second connection of supplying with exhaust port 57b are cut off by the second circular bead surface 53c, and second supplies with exhaust port 57b and the first annular slot 53b(through hole 53j) under the less state of opening area each other, start to be communicated with, and be communicated with drain tap 58 via via hole 53i, so the second supply exhaust port 57b and drain tap 58 start to be communicated with.

Thus, because the second control grease chamber 32 is communicated with drain tap 58, therefore the second control grease chamber 32 becomes low pressure, is the application of force of spring 18 to the active force of cam ring 17.Therefore, the spring force that exceedes spring 18 is pressed in the first discharge of controlling in grease chamber 31, cam ring 17 to counterclockwise in rotary moving, moves to the direction that reduces offset as shown in Figure 9, becomes the state of the high voltage control of the smooth and homogeneous shown in the internal-combustion engine rotational speed d of Figure 10.

Like this, by the work of described pilot valve 50, in the time that pump is discharged the high voltage control of pressing, can suppress oil pressure and excessively rise.

,, in the case of the existing variable capacity type oil pump without pilot valve 50, shown in the solid line of Fig. 6, in the time of oil pressure control, oil pressure rises along with the rise of rotational speed of internal-combustion engine as the aforementioned.This be because, internal-combustion engine rotational speed need to further reduce the offset of cam ring 17 while rising, but discharge the amount of the spring constant of pressing the spring 18 that only rises.

In contrast, in the present embodiment, owing to thering is described pilot valve 50, therefore pump is discharged and is pressed while too reduction, and guiding valve 53 upward (direction of taking a seat) is mobile, makes connection mouth 56 and second supply with exhaust port 57b and is communicated with, import oil pressure to the second control grease chamber 32 and come the spring force of secondary spring 18, described cam ring 17 is moved to the large direction of eccentric quantitative change, therefore, discharge and press liter.

If discharging to press too, pump rises, the spring force that guiding valve 53 is resisted valve spring 54 declines mobile, make drain tap 58 and second supply with exhaust port 57b and be communicated with, reduced pressure in the second control grease chamber 32, the offset of controlling cam ring 17 makes it compared with little and reduce oil pressure.These controls just can be carried out by the small movement of guiding valve 53, so the impact of the spring constant of valve spring 54 is less, as shown in the d region of Figure 10, oil pressure can be controlled to the roughly discharge of P2 with smooth state and presses.

And, in the present embodiment, at the internal-combustion engine rotational speed shown in Figure 10 under b zone state and d zone state, as shown in Fig. 8 and Fig. 9, the first circular bead surface 53a of described guiding valve 53 and the second circular bead surface 53c make the opening area of the first supply exhaust port 57a and the opening area of the second supply exhaust port 57b relatively to contrary size variation.That is, make the import volume that the discharge of the first control grease chamber 31 is pressed and discharge from the second control grease chamber 32 oil pressure discharge capacity relativity change, therefore, realized the stabilization of the smooth discharge pressure-controlled of described P1 and P2.

In addition, in the present embodiment, be made as simultaneously the period of utilizing the first circular bead surface 53a of guiding valve 53 and the second circular bead surface 53c to make to switch each mouthful, but also can have the state that makes both sides be communicated with simultaneously or both sides are cut off simultaneously.

In addition, first, second circular bead surface 53a, the 53c of guiding valve 53 and the border of the first path axial region 53b also can form chamfering or R shape.These are the stroke of guiding valve 53 and the key elements of opening area characteristic that change while switching, are regulated by pump capacity or switching pressure.

Figure 11 (A)～(C) represents to supply with the A/F W1 of an end opening of the first supply exhaust port 57a that drain passageway 6a is communicated with and the various structure of the width W 2 of the first circular bead surface 53a with described first, in structure shown in Figure 11 (A), the A/F W1 of the first supply exhaust port 57a and the width W 2 of the first circular bead surface 53a are set as roughly equal.In structure shown in Figure 11 (B), the width W 2 of the first circular bead surface 53a is formed as more bigger than the A/F W1 of the first supply exhaust port 57a.In structure shown in Figure 11 (C), the first A/F W1 that supplies with exhaust port 57a is formed as more bigger than the width W of the first circular bead surface 53a 2.

Like this, by relativity change the first A/F W1 of supply exhaust port 57a and the width W 2 of the first circular bead surface 53a, can at random control the delivery volume of controlling the oil pressure of supplying with grease chamber 31 to described first according to the stroke amount of described guiding valve 53.

Figure 12 (A)～(C) as with Figure 11, change the size of the A/F W1 of an end opening of described the first supply exhaust port 57a, on the other hand, position up and down at the first circular bead surface 53a outer circumferential face forms chamfered section 53k, 53l, and the width W 1 of the central position 53m between this chamfered section 53k, 53l is set as equating.

; in structure shown in Figure 12 A; the first A/F W1 that supplies with exhaust port 57a mono-end opening is set as with the width W 3 of the central position 53m of the first circular bead surface 53a roughly the same; in structure shown in Figure 12 B; the first A/F W1 that supplies with exhaust port 57a is set as less than the width W 3 of the first circular bead surface 53a central position 53m; in addition, in the structure shown in Figure 12 C, the first A/F W1 that supplies with exhaust port 57a is set as larger than the width W 3 of the central position 53m of the first circular bead surface 53a.In the case of the width W 3 of the central position 53m of described the first circular bead surface 53a is larger than A/F W1, also there is small gap in central position 53m and first end opening of supplying with exhaust port 57a, and tripartite also can not be completely severed.These width are the factors that change the displacement of guiding valve 53 and the relation of open communication area change, when the opening area of pilot introducing port 55 sides changes in the ban, the opening area of the first annular slot 53g side of the opposing party changes on the contrary, the size of pressing according to the specification of pump main body and work and in good time choice for use.

First supplies with in the situation identical with the width of the first circular bead surface 53a of the aperture of exhaust port 57a, or in the case of the wider width of the first circular bead surface 53a, with slide with the situation that the length of the micro-gap in hole 52 similarly changes be also the identical meaning.

And the second circular bead surface 53c is also the same with the second relation of supplying with exhaust port 57b with variation.

In addition, with regard to the energising switching time of described electromagnetic switching valve 40, judged according to the operating condition of internal-combustion engine by described controller unit, but be not limited to the state shown in Figure 10, also can be the situation that converts the state of c from the state of internal-combustion engine rotational speed a to, can be also the situation that converts the state of d from the state of b to.

Conventionally, in the time of High Rotation Speed, require the oil pressure that requires of the injection pressure of oil nozzle or crankshaft bearing, therefore,, in the time of internal-combustion engine low speed rotation, switch on and form low voltage control to electromagnetic switching valve 40, prevent that oil pressure from rising to realize the minimizing of consumption of power, and in the time of High Rotation Speed, electromagnetic switching valve 40 is made as to non-energising, and switches to high voltage control, discharge is pressed and be raised to the level needing, obtain the characteristic as shown in the solid line of Fig. 6.

And the internal-combustion engine rotational speed that switches the energising of described electromagnetic switching valve 40 can change according to the operating condition of internal-combustion engine, as mentioned above, described controller unit judges internal-combustion engine rotational speed, load, profit temperature etc. as parameter.

For example, in the time of high load or when high oil temperature, switch to high voltage control from low speed rotation, oil nozzle is sprayed, can prevent pinking, so can make igniting reduce in advance fuel consumption opportunity.In addition, in the time of low oil temperature, maintain low voltage control, reduce consumption of power or stop coming the injection of flow bean, can shorten preheat time and reduce HC(hydrocarbon) discharge.

But, under the state of internal-combustion engine High Rotation Speed region and high oil pressure control, it is large that the pulse pressure of main oil gallery 05 becomes, in the time that pulse pressure acts on first, second and controls grease chamber 31,32, sometimes become following problem: cam ring 17 vibrates, the discharge pulse pressure of pump is exaggerated and produces noise or vibration.

Control 32 both sides of grease chamber and supply with under the state of high oil pressure controlling grease chamber 31 and second to described first, because pulse pressure acts on similarly, therefore, because of the consistent pulse pressure of phase place, cam ring 17 is unstable and vibrate sometimes.

But, in the present embodiment, the second oil purifier 2 is arranged on from the downstream side of the first tributary circuit 3 of main oil gallery 05 branch, and is arranged on 4 points of the first tributary circuit 3 and the second tributary circuits and supports the front, therefore, can utilize the resistance of the second oil purifier 2 to make branch's attenuate pulsations before.

Consequently, can reduce comparably the pulse pressure of the first control grease chamber 31 and the second control grease chamber 32.Like this, owing to can reducing comparably the pulse pressure of two control grease chambeies 31,32, which pulse pressure that therefore can not control grease chamber 31,32 becomes large and balance is gone to pot, and can make the mobile stabilization of cam ring 17.

In addition, in the time that electromagnetic switching valve 40 faults etc. are abnormal, are necessary to take into account pump under the state of combustion machine High Rotation Speed, high load, high oil temperature and discharge the functional reliability that presses to high voltage control.First, be, that under non-power status, solenoid open pore 42a and connecting port 45 are communicated with at electromagnetic coil, so that oil pressure is imported into the second control grease chamber 32 in the time of the fault such as coil or electrical wiring harness broken string of electromagnetic switching valve 40.

Owing to being provided with the second oil purifier 2 in the upstream of described electromagnetic switching valve 40, can prevent that pollutant from stopping up and causing that the work of electromagnetic switching valve 40 is bad, in the time of non-energising, can prevent that the second control grease chamber 32 is communicated with draining path 5.

Owing to being provided with the first oil purifier 1 between oil pump 10 and main oil gallery 05, therefore pollutant can not flow to main oil gallery 05 or the first tributary circuit 3 conventionally.

But the first oil purifier 1 is in the time producing filter net jam etc., in order to protect internal-combustion engine, diverter valve 09 is opened, and therefore, now pollutant may flow into the first tributary circuit 3 sides.

But due between first 1 stage of replacement of oil purifier setting and less produce above-mentioned situation, therefore compared with the first oil purifier 1, the second oil purifier 2 can be small-sized and without the oil purifier of changing.

In addition, even in aforesaid situation, the second oil purifier 2, as long as can trap the big or small pollutant that is tangled and make its pinning by ball valve 43 in electromagnetic switching valve 40, therefore can be set as than the large mesh size of the first oil purifier 1.

If the first oil purifier 1 long time running and second oil purifier 2 under the state of being shunted also stop up, because the path of supporting the front that divides at the first tributary circuit 3 and the second tributary circuit 4 is just cut off, therefore oil pressure all can not import the first control grease chamber 31, the second control grease chamber 32.

In this case, due to the load on spring of spring 18, cam ring 17 forms maximum eccentricity amount, and forms the state of maximum capacity and remain unchanged, and therefore can maintain high oil pressure.

Because be also that non-energising all maintains high oil pressure no matter described electromagnetic switching valve 40 is switched on, so even if the fault of electromagnetic switching valve 40 repeats also can maintain high oil pressure.

And, for excessive oil pressure, can make the one-way valve work of diverter valve 09 and suppress the breakage of the each part in oil pump 10 or oil hydraulic circuit.

In addition, the in the situation that of high oil pressure state continuance, control all side clearance and exhaust port 34 adjacency between each ring portion 19,19 and the pump housing 1, cap assembly 12 of grease chamber 32 because first controls grease chamber 31 and second, so oil may leak and flow into the first control grease chamber 31 and the second control grease chamber 32.

Because the second oil purifier 2 stops up, oil flows out from described sealed member 30,30 suction sides to low voltage section, but many because flow into quantitative change, rises so the first control grease chamber 31 and second controls the oil pressure of grease chamber 32.

Under the state that is non-energising at described electromagnetic switching valve 40, the first control grease chamber 31 and second controls grease chamber 32 and is communicated with first and second tributary circuit 3,4 via electromagnetic switching valve 40 and pilot valve 50, so become same oil pressure.When rise to regulation oil pressure as above under same oil pressure state time, cam ring 17 starts to move to clockwise direction, can control in high pressure side to discharge and press.

In addition, when the first oil purifier 1 stops up, because the oil pressure of main oil gallery 05 reduces, so the oil pressure of the oil pressure ratio main oil gallery 05 of first, second control grease chamber 31,32 is high, oil is controlled grease chamber 31,32 from first, second and is flowed to main oil gallery 05, can once remove the pollutant that gets lodged in the second oil purifier 2.

(fault diagnosis)

In said embodiment, can utilize the oil pressure sensor or the oil pressure switch that are arranged at main oil gallery 05 to carry out fault diagnosis.Be redefined in the time that electromagnetic switching valve 40 is switched on, under the internal-combustion engine rotational speed stipulating and oil temperature, become below the oil pressure of regulation.In addition, be redefined in the time of the non-energising of electromagnetic switching valve 40, become the oil pressure of regulation under the internal-combustion engine rotational speed stipulating and oil temperature more than.

In the case of instruction with respect to sending to described electromagnetic switching valve 40 exist different from predefined oil pressure, be judged as certain fault occurred, open emergency warning lamp etc. and by electromagnetic switching valve 40 in non-power status, to form high voltage control state.

Below, the technological thought beyond the described invention of grasping from described mode of execution is described.

(aspect a)

A kind of variable capacity type oil pump, is characterized in that possessing:

The rotor being driven in rotation;

Multiple blades, it is come in and gone out and is located at freely this rotor periphery;

Cam ring, it holds described rotor and blade and forms multiple pump chambers in inner circumferential side, and, change the center of inner peripheral surface with respect to the offset of the rotating center of described rotor by mobile;

Sucting, the described pump chamber opening that when it carries out eccentric move with respect to the rotating center of described rotor to a direction to described cam ring, volume increases;

Discharge portion, the described pump chamber opening of volume reducing it carries out eccentric movement during to described cam ring to other direction;

Force application part, its to described cam ring with respect to the large direction of the eccentric quantitative change of the rotating center of described rotor to the described cam ring application of force;

First controls grease chamber, and it is given described cam ring and make the other direction that described cam ring diminishes to offset carry out eccentric mobile power by being imported into via importing path the application of force that discharge pressure is resisted described force application part from described discharge portion;

Second controls grease chamber, and it is by being imported into working oil, and the application of force cooperation of described force application part, gives the power that described cam ring is moved to a direction;

Switching mechanism, it switches to via the access that is communicated with described discharge portion and the second control grease chamber and controls to described second the state that grease chamber imports the state of working oil and discharges working oil via described access from the second control grease chamber;

Control mechanism, its discharge according to described discharge portion presses to the first control grease chamber supply discharge pressure maybe will supply with cut-out, and supply with or discharge oil pressure to described the second control grease chamber via described access,

Described control mechanism is configured to, in the case of the discharge pressure ratio of described discharge portion require to discharge press high, supply with to discharge to the first control grease chamber and press, and discharge the second working oil of controlling in grease chamber.

(aspect b) variable capacity type oil pump as described in first aspect, is characterized in that,

Described switching mechanism is by the solenoid electric valve of electric switching controls.

(aspect c) variable capacity type oil pump as described in the third aspect, is characterized in that,

Under described the second state, when the spring force of resisting described control spring when described guiding valve moves to other direction, the described first opening area of supplying with exhaust port changes in the mode diminishing, and becomes large from the described second opening area of controlling mouthful circulation flow path to drain tap.

(aspect d) variable capacity type oil pump as described in aspect c, is characterized in that,

Under described the second state, when the spring force of resisting described control spring when described guiding valve moves to other direction, described first supplies with the opening area of exhaust port changes in the mode diminishing, and is controlling mouthful to the circulation flow path opening of drain tap from described second, and it is large that this opening area becomes.

(aspect e) variable capacity type oil pump as described in aspect d, is characterized in that,

Under described the second state, in the time that the spring force of guiding valve opposing control spring moves to other direction, the described first opening area of supplying with exhaust port diminishes and closes, then, from described the second control mouthful circulation flow path opening to drain tap, and this opening area changes to become large mode.

(aspect f) variable capacity type oil pump as described in the third aspect, is characterized in that,

Described guiding valve is formed with the via hole of the hollow shape of an axial distolateral opening, this via hole open one distolaterally dispose described control spring, and, be communicated with described via hole from being radially formed through in another distolateral through hole, form from described second and control mouth to the circulation flow path drain tap by this through hole and via hole.

(aspect g) variable capacity type oil pump as described in either side in aspect 1～f, is characterized in that,

The oil of discharging from described discharge portion is the lubrication oil of internal-combustion engine.

(aspect h) variable capacity type oil pump as described in either side in aspect 1～g, is characterized in that,

The oil of discharging from described discharge portion be internal-combustion engine variable valve gear driving oil and spray the cooling oil for piston by oil nozzle.

Claims (11)

1. a variable capacity type oil pump, is characterized in that, possesses:

The rotor being driven in rotation;

Multiple blades, it is come in and gone out and is located at freely the periphery of this rotor;

Cam ring, it holds described rotor and blade and forms multiple pump chambers in inner circumferential side, and, change the center of inner peripheral surface with respect to the offset of the rotating center of described rotor by mobile;

Sucting, the described pump chamber opening that when it carries out eccentric move with respect to the rotating center of described rotor to a direction to described cam ring, volume increases;

Discharge portion, the described pump chamber opening of volume reducing it carries out eccentric movement during to described cam ring to other direction;

Force application part, its to described cam ring with respect to the large direction of the eccentric quantitative change of the rotating center of described rotor to the described cam ring application of force;

First controls grease chamber, and it is given described cam ring and make the other direction that described cam ring diminishes to offset carry out eccentric mobile power by importing via importing path the application of force that discharge pressure is resisted described force application part from described discharge portion;

Second controls grease chamber, and it cooperates with the application of force of described force application part by being imported into working oil, gives the power that described cam ring is moved to a direction;

Switching mechanism, it switches to via the access that is communicated with described discharge portion and the second control grease chamber and controls to described second the state that grease chamber imports the state of working oil and discharges working oil via described access from the second control grease chamber;

Become the work of minimum advancement row at the offset of described cam ring, along with described discharge presses change large, the opening area of described access changes, and discharges the described second opening area of controlling the drain passageway of the working oil in grease chamber and is changed to contrary with the opening area of described importing path.

2. variable capacity type oil pump as claimed in claim 1, is characterized in that,

Described switching mechanism is by the solenoid electric valve of electric switching controls.

3. a variable capacity type oil pump, is characterized in that, possesses:

The rotor being driven in rotation;

Multiple blades, it is come in and gone out and is located at freely the periphery of this rotor;

Cam ring, it holds described rotor and blade and forms multiple pump chambers in inner circumferential side, and, by moving the center that changes inner peripheral surface with respect to the offset in the rotation of described rotor;

Sucting, the described pump chamber opening that when it carries out eccentric move with respect to the rotating center of described rotor to a direction to described cam ring, volume increases;

Discharge portion, the described pump chamber opening of volume reducing it carries out eccentric movement during to described cam ring to other direction;

Force application part, its to described cam ring with respect to the large direction of the eccentric quantitative change of the rotating center of described rotor to the described cam ring application of force;

First controls grease chamber, and it presses the application of force of resisting described force application part by being imported into from described discharge portion to discharge, and gives described cam ring and makes the other direction that described cam ring diminishes to offset carry out eccentric mobile power;

Second controls grease chamber, and it cooperates with the application of force of described force application part by being imported into working oil, gives the power that described cam ring is moved to a direction;

Switching mechanism, it switches to via the access that is communicated with described discharge portion and the second control grease chamber and controls to described second the state that grease chamber imports the state of working oil and discharges working oil via described access from the second control grease chamber;

Control mechanism, comprise: valve body, it is formed with respectively the introducing port that imports described discharge and press, control with described first that grease chamber is communicated with first control mouthful, the second control mouth being communicated with via described access and described the second control grease chamber side, the connecting port being communicated with the described switching mechanism side of described access, the drain tap that can be communicated with the second control mouth; Guiding valve, it is located in this valve body sliding freely, controls the connected state of each mouthful; Control spring, its with than the little application of force of the application of force of described force application part to a direction to this guiding valve application of force;

At described guiding valve by the described control spring application of force and to a direction the largest mobile initial position, become described introducing port by this jammed spool valve, and described first controls mouth and drain tap connection, described second controls the first state of mouth and connecting port connection, discharge to press and increase and oil pressure in described introducing port uprises, when the application of force that described guiding valve is resisted described control spring thus moves to other direction, become described introducing port and the first control mouthful connection, and the second state of described the second control mouth and drain tap connection;

When the spring force of resisting described control spring when described guiding valve moves to other direction, be changed to the opening area of controlling mouthful with described first to contrary size from the described second opening area of controlling mouthful circulation flow path to drain tap.

4. variable capacity type oil pump as claimed in claim 3, is characterized in that,

Under described the second state, when the spring force of resisting described control spring when described guiding valve moves to other direction, the described first opening area of controlling mouthful changes in the mode diminishing, and becomes large from the described second opening area of controlling mouthful circulation flow path to drain tap.

5. variable capacity type oil pump as claimed in claim 4, is characterized in that,

Under described the second state, when the spring force of resisting described control spring when described guiding valve moves to other direction, the described first opening area of controlling mouthful changes in the mode diminishing, and is controlling mouthful to the circulation flow path opening of drain tap from described second, and it is large that this opening area becomes.

6. variable capacity type oil pump as claimed in claim 5, is characterized in that,

Under described the second state, resist the spring force of described control spring and other direction while moving when guiding valve, the described first opening area of supplying with exhaust port diminishes and closes, afterwards, from described the second control mouthful circulation flow path opening to drain tap, and its opening area changes to become large mode.

7. variable capacity type oil pump as claimed in claim 6, is characterized in that,

The oil of discharging from described discharge portion is the lubrication oil of internal-combustion engine.

8. variable capacity type oil pump as claimed in claim 7, is characterized in that,

The oil of discharging from described discharge portion be internal-combustion engine variable valve gear valve driving oil and sprayed and for the cooling oil of piston by oil nozzle.

9. variable capacity type oil pump as claimed in claim 3, is characterized in that,

Described guiding valve is formed with the via hole of the hollow shape of an axial distolateral opening, this via hole open one distolaterally dispose described control spring, and, be communicated with described via hole from being radially formed through in another distolateral through hole, form from described second and control mouth to the circulation flow path drain tap by this through hole and via hole.

10. a variable capacity type oil pump, is characterized in that, possesses:

Pump structure body, it discharges by being driven in rotation the volume-variation that makes multiple work grease chamber the oil being imported into from sucting from discharge portion;

Changeable mechanism, it moves by movable member, changes to the volume-variation amount of the described work grease chamber of described discharge portion opening;

Force application part, its under the state of giving described movable member load on spring to the large direction application of force of volume-variation quantitative change of the described work grease chamber at described discharge portion opening;

First controls grease chamber, and it is pressed by being imported into from the discharge of described discharge portion, makes the masterpiece of direction of the application of force of resisting described force application part for described changeable mechanism;

Second controls grease chamber, and it makes with the equidirectional masterpiece of the application of force of described force application part for described changeable mechanism by being imported into working oil;

Switching mechanism, it switches to and imports the state of controlling the working oil in grease chamber than the state of the working oil of described discharge pressure decompression and discharge described second from described discharge portion to the second control grease chamber;

Control mechanism, has: first throttle portion and the second restriction, and described first throttle portion utilizes described changeable mechanism to become the work of minimum advancement row in the volume-variation amount of described work grease chamber, becomes large along with discharging to press, and orifice size is increased; Described the second restriction reduces orifice size;

Utilize the side in described first throttle portion and described the second restriction, carry out throttling to controlling to described second the working oil of supplying with grease chamber from described switching mechanism, utilize the opposing party to carry out throttling to controlling the working oil of discharging to low voltage section grease chamber from described second.

11. 1 kinds of variable capacity type oil pumps, is characterized in that possessing:

The rotor being driven in rotation;

Multiple blades, it is come in and gone out and is located at freely the periphery of this rotor;

Cam ring, it holds described rotor and blade and forms multiple pump chambers in inner circumferential side, and by moving the center that changes inner peripheral surface with respect to the offset in the rotation of described rotor;

Sucting, the described pump chamber opening that when it carries out eccentric move with respect to the rotating center of described rotor to a direction to described cam ring, volume increases;

Discharge portion, the described pump chamber opening of volume reducing it carries out eccentric movement during to described cam ring to other direction;

Force application part, its to described cam ring with respect to the large direction of the eccentric quantitative change of the rotating center of described rotor to the described cam ring application of force;

First controls grease chamber, and it is given described cam ring and make the other direction that described cam ring diminishes to offset carry out eccentric mobile power by importing via importing path the application of force that discharge pressure is resisted described force application part from described discharge portion;

Second controls grease chamber, and it cooperates with the application of force of described force application part by being imported into working oil, gives the power that described cam ring is moved to a direction;

Switching mechanism, it switches to via the access that is communicated with described discharge portion and the second control grease chamber and controls to described second the state that grease chamber imports the state of working oil and discharges working oil via described access from the second control grease chamber;

Control mechanism, its discharge according to described discharge portion presses to the first control grease chamber and supplies with discharge pressure or sever supply, and controls grease chamber via described access to described second and supply with or discharge oil pressure;

Described control mechanism is configured to, in the case of the discharge pressure ratio of described discharge portion require to discharge press high, supply with to discharge to the first control grease chamber and press, and, the working oil in the second control grease chamber is discharged.

Images